Form feed device with variable split

ABSTRACT

Form feed device for bookkeeping machines and the like which allows the spacing of two forms of equal or of different width which are positioned side by side, with the spacing of both forms occurring simultaneously or of either one of the two forms alone, and with provisions for making the split variable by the operator when form sizes are to be changed.

[ Nov. 26, 1974 FORM FEED DEVICE WITH VARIABLE References Cited SPLIT [75] Inventors: James Downie, Cumbernauld,

0X H9 6m 2/ 26 .2 2 S T NW N I E u T m A m" P mm S .m E m Tlk mm T nm SFB D fim n99 NHH U l O2 73 44 L 23 England; Vijai Prakash, Larbert, Scotland [73] Asslgnee: ggg Corporamn Detrolt Primary Examiner-Richard A. Schacher Attorney, Agent, or Firm-Karl H. R. Stoess [221 Filed: Aug. 6, 1973 ABSTRACT [21] Appl. No.: 386,094

Form feed device for bookkeeping machines and the [30] Foreign Application Priority Data like which allows the spacmg of two forms of equal or Oct. 13, 1972 Great Britain.............

of different width which are positioned side by side,

with the spacing of both forms occurring simultaneously or of either one of the two forms alone, and

with provisions for making the split variable by the op- B65h 17/20 erator when form sizes are to be changed. 226/174, 179, 180, 176, 226/177, 181

Int.

[ [58] Field of Search 185 I90, 109, HO 6 Claims, 10 Drawing Figures PATENTEL HOV 2 61974 SHEET 1 OF 2 FiGJC.

' FIG. IB.

FIG. IA.

FORM FEED DEVICE WITH VARIABLE SPLIT SUMMARY OF THE INVENTION The principal object of the invention is to provide a plurality of pressure roll assemblies (units) which are spaced along the drive roll of a bookkeeping machine and are adapted to either press upon an inserted card (form) so that it is spaced by the drive roll or left stationary when the drive roll is actuated.

Another object is to make these units operatoradjustable so that any number of them which correspond to the width of the respective form can be set in such a manner that the form which is engaged by the units can be caused to space or not to space just as is desired for the operating mode of the machine. This feature allows the adaptation of the bookkeeping machine by the operator to forms having another width than those previously used. Thereby subsequent field service is avoided in case of a change of form widths, and the necessity for a new custom-built front feed device is eliminated.

Still another object of the invention is the use of a single prime mover to drive the two movable parts of the form feed device, i.e. thedrive roll and the open/close camshaft.

Devices for achieving the purpose of this invention are known in the form of split platens, each portion of which requires a separate prime mover. Also known are dual drive rolls which provide variable split but as in the split platen apparatus require use of either two clutches or two prime movers. In addition, this known drive occupies more space which reduces accessibility and visibility. Such arrangements are complex and costly.

DESCRIPTION OF THE DRAWINGS FIGS. 1 a-c are schematic illustrations of different combinations of spacing of the improved form feed device with variable split.

FIG. 2 shows a single pressure roll assembly in one of two possible operating positions. shows the assembly of FIG. 2 in cross section along the line 3-3 in FIG. 2.

FIGS. -11 show the special cam means which enable a pressure assembly (unit) to either exert pressure on the drive roll for spacing a form or not to exert pressure thereon (form not spaced). In FIG. 4a one form is moved, whereas the other one is not. In FIG. 4b neither form is moved (open position). In FIG. 40 both forms are moved (closed position). In FIG. 4d the operation is reversed from the one in FIG. 4a.

FIG. 5 illustrates in simplified form the single prime mover as arranged for driving both the driving roll and the open/close camshaft.

DESCRIPTION OF THE PREFERRED EMBODIMENT FIGS. I u-c illustrate in form of an example how a certain plurality of pressure roll assemblies (units), l0-l7, are uniformly distributed along the length of a drive roll 20. The structure of each one of the units 10-17 is shown in FIGS. 2 and 3.

In FIG. la the five units 10, 11, I2, 13, 14 which are used to space a form A and the three units l5, 16, 17 which are used to space another. narrower form B all function in the same manner, i.e., by exerting friction pressure upon the form against the drive roll so that both forms (A and B) are spaced upon actuation of the drive roll 20 by the drive shown in FIG. 5.

In FIG. lb the five units 10-14 function so as to exert pressure asainst the drive roll 20 so that form A is spaced when the drive roll is driven, whereas the units 15-17 carry out the opposite mode of operation, i.e., not exerting pressure upon the drive roll so that form B is not spaced when the drive roll 20 is driven.

In FIG. 1c the form B is spaced, whereas the form A remains stationary upon actuation of the drive roll. To achieve this, the mode of operation of the two groups of units 10-14 and 15-17 has to be reversed, respectively, as compared with that shown in FIG. 1b.

By turning to FIGS. 2 and 3 it will now be explained how each unit 10-17 is composed and how its mode of operation is set. Each of the identical units 10-17 is anchored with a support bracket 19 in a base rail 22 of the bookkeeping machine, which rail is fixedly spaced from and extends parallel to the drive roll 20. Each of the units 10-17 is firmly embedded in the base rail 22 and can therefore not be shifted laterally.

As seen in FIGS. 2 and 3 there is an open/close (0 c) camshaft 24 near the base which is driven by the same prime mover as the drive roll 20. On a pivot shaft 26 a bifurcated pressure roll arm 28 is fixed which carries a pressure roll 30 at one end and a cam roll shaft 32 with a shiftable cam roll 34 on the other end thereof.

The cam roll 34 which is adapted to be shifted manually by the operator either toward the left or toward the right can thus engage either a cam 36 or a cam 38 (the latter position is shown in FIG. 2 and FIG. 3. These two cams are fixedly attached to the ole camshaft 24 which is adapted for counterclockwise rotation allowing it to assume either one of four different stop positions (FIGS. 4 41-11). The two cams 36 and 38 are identical but are out of phase with each other.

To make engagement between the shiftable cam roll 34 of each unit and one of the cams 36 or 38 possible, pressure spring means 40 are provided which are anchored with one end in the base rail 22 and whose other end presses against the platen-engaging end of the bifurcated, pivotable pressure roll arm 28. Ifthe cam roll 34 is engaging cam 38 (as shown in FIG. 2); the pressure roll 30 is closed in that it is pressed against the drive roll 20 (closed position). However, if the cam roll 34 is in its other position, i.e., against cam 36, the pressure roll arm 28 is lifted upward and the pressure roll does not engage the drive roll 20 (open position).

Each unit is further provided with a brake arm 42 which is lightly sprung against a fixed brake bar 44 positioned above the drive roll 20. Brake arm spring means 46 urge the brake bar 42 against the brake bar 44. The force between brake arms and brake bar is sufficient to hold the form in position when the correspoh'dihg'piess'ar"ME are in the open state, but allows the form to slide between brake arms and brake when the corresponding units are in the closed (drive) state.

Above the guide bar 44 there is a platen bar 48.

FIG. 5 shows a stepper motor 50 on a stepper motor shaft 51. On said shaft on each side of the stepper motor there is a clutch (52, 54). One of these clutches (52) is a clockwise transmitting unidirectional clutch. It transfers drive from the stepper motor 50 via a driving wheel 56 and a belt 58 to a driven wheel 57 on the drive roll 20. The other clutch (54) is a counterclockwise transmitting unidirectional clutch which transfers drive from the stepper motor via a driving wheel 59 and a belt 60 to a driven wheel 61 on the open/close camshaft 24.

Operation As the camshaft 24 has only four stop positions and always rotates in steps of 90 or multiples of 90 degrees, all cam rolls 34 in line with cam 36 operate in phase with each other while those in line with cam 38 also operate in phase with each other, but 90 degrees out of phase with these in line with cams 36. The operator can manually preposition each cam roll 34 either in line.

with cams 36 or cams 38. In this manner the operator can choose the split by positioning all cam rolls 34 on one side of the bookkeeping machine, say left hand, in line with earns 36 and all cam rolls 34 on the other side, right hand, of the split between two forms to be inserted, in line with cams 38. Now, if the two forms are placed into the machine, vertical line spacing of the forms will be as follows (see FIG. 4):

Cam shaft position a right hand form spaces, left hand form stationary; Cam shaft position b none of the forms spaces because all units are open; Cam shaft position both forms space because all units are closed; Cam shaft position d right hand form stationary, left hand form spaces. It is reiterated that form spacing drive is only transmitted where a pressure roll 30 of a unit is in springbiased contact with the drive roll 20 (closed position).

As shown in FIG. drive from the stepper motor 50 is taken through the clockwise transmitting unidirectional clutch 52 to the drive roll 20, while drive to the 0/0 camshaft 24 is taken through a counterclockwise transmitting unidirectional clutch 54. Thus the complete control of two side-by-side forms is achieved by driving the motor counterclockwise until the 0/1 camshaft is in one of its four positions to provide the required spacing sequence. Now, the form or forms, as the case may be, can be spaced by driving the motor in clockwise direction with the cam shaft remaining stationary. Control of the motor is by closed loop from both output members (o/c camshaft and drive roll).

Forms may be manually inserted into the device when the corresponding pressure rolls 30 are open, by sliding the forms between the brake arms 42 and the brake bar 44.

The special advantage of the improved form feed device lies in the fact that the split is variable, i.e., the operator can select how many of the units which are evenly distributed along the base bar 22 can be set one way and how many the other way. This difference in setting is chosen in accordance with the width of the two forms to be inserted. lf both forms are of equal width, an equal number of units on each side are set one and the other way; respectively. lf the forms are of unequal width (FlGS. la-c), the (larger) number of units covering the width of the wider form is set one way, and the (smaller) number of units covering the width of the narrower form is set the other way.

The number of units (pressure roll assemblies) which are distributed along the base bar is immaterial. In the example of H6. 1 this number is 8. It would allow the following form-width operating arrangement by setting the cam rolls 34 accordingly:

1. one form width covering two units, the other one six;

2. one form width covering three units, the other one five;

3. one form width covering four units, the other one also four.

While the invention has been described with respect to the preferred embodiment thereof, it will be understood that the invention and its various features are capable of changes and variations which are within the spirit and scope of the following claims.

What is claimed is:

1. In a form feed device of a bookkeeping machine having spaced from each other and in horizontal extension, parallel means comprising drive roll means, rotatable cam shaft means and a base,

a plurality of pressure roll assemblies spacedly arranged along said parallel means,

each of said assemblies comprising in combination: support means being attached to said base, two cams fixed on said cam shaft means. said cam shaft means extending through all of said assemblies, with said cams being out of phase with respect to each other, pressure roll carrying means pivotally arranged in said assembly, said pressure roll carrying means having a pressure roll at the end which faces the drive roll means and a horizontally shiftable cam roll means on the other end, said cam roll means being shiftable against either one of the two cams, and means biasing said pressure roll carrying means against the drive roll means.

2. The device as claimed in claim 1, further having means for setting said cam shaft means in different positions so as to allow a choice of two tyes of engagement between said cams and said shiftable cam roll maans with the result that any desired spacing condition can be created by either causing friction engagementor non-engagement between the pressure roll and the drive roll means.

3. The device as claimed in claim 2, further having a prime mover cooperating with a clockwise and a counterclockwise unidirectional clutch, said prime mover being operatively connected via said clutches with the drive roll means and the rotatable cam shaft means.

4. In a form feed device for two forms having spaced from each other and in horizontal extension parallel means comprising a rotatable drive roll, a rotatable open/close cam shaft, a pivot shaft and a base rail,

a plurality of pressure roll assemblies spacedly arranged along said four parallel means, each of said assemblies comprising in combination: a support bracket which is embedded in said base rail, two cams carried on said open/close cam shaft which horizontally extends through all of said assemblies, and said cams being fixed thereon 90 out of phase with respect to each other, a pressure roll arm arranged on said pivot shaft, said pressure roll arm having a pressure roll facing the drive roll at one end and a horizontally shiftable cam roll on the other end, said cam roll being adapted to be shifted against either one of the two cams, and pressure means resiliently urging said pressure roll arm against the drive roll so that the pressure roll presses against the drive roll if the cam roll is placed to engage one of said cams, but does not ing a stepping motor shaft, a stepper motor thereon, a first clockwise transmitting unidirectional clutch on one side of the stepper motor, said first clutch transmitting clockwise torque to the drive roll, and a second, counterclockwise transmitting unidirectional clutch on the other side of said stepper motor, said second clutch transmitting counterclockwise torque to the open/close 

1. In a form feed device of a bookkeeping machine having spaced from each other and in horizontal extension parallel means comprising, drive roll means, rotatable cam shaft means and a base, a plurality of pressure roll assemblies spacedly arranged along said parallel means, each of said assemblies comprising in combination: support means being attached to said base, two cams fixed on said cam shaft means, said cam shaft means extending through all of said assemblies, with said cams being 90* out of phase with respect to each other, Pressure roll carrying means pivotally arranged in said assembly, said pressure roll carrying means having a pressure roll at the end which faces the drive roll means and a horizontally shiftable cam roll means on the other end, said cam roll means being shiftable against either one of the two cams, and means biasing said pressure roll carrying means against the drive roll means.
 2. The device as claimed in claim 1, further having means for setting said cam shaft means in different positions so as to allow a choice of two types of engagement between said cams and said shiftable cam roll maans with the result that any desired spacing condition can be created by either causing friction engagement or non-engagement between the pressure roll and the drive roll means.
 3. The device as claimed in claim 2, further having a prime mover cooperating with a clockwise and a counterclockwise unidirectional clutch, said prime mover being operatively connected via said clutches with the drive roll means and the rotatable cam shaft means.
 4. In a form feed device for two forms having spaced from each other and in horizontal extension parallel means comprising a rotatable drive roll, a rotatable open/close cam shaft, a pivot shaft and a base rail, a plurality of pressure roll assemblies spacedly arranged along said four parallel means, each of said assemblies comprising in combination: a support bracket which is embedded in said base rail, two cams carried on said open/close cam shaft which horizontally extends through all of said assemblies, and said cams being fixed thereon 90* out of phase with respect to each other, a pressure roll arm arranged on said pivot shaft, said pressure roll arm having a pressure roll facing the drive roll at one end and a horizontally shiftable cam roll on the other end, said cam roll being adapted to be shifted against either one of the two cams, and pressure means resiliently urging said pressure roll arm against the drive roll so that the pressure roll presses against the drive roll if the cam roll is placed to engage one of said cams, but does not press against the drive roll if it is placed against the other one of said cams.
 5. The device as claimed in claim 4, wherein said open/close cam shaft with a set of cams for each pressure roll assembly is adapted to be set in four different positions which in accordance with the respective setting of the cam rolls of the pressure roll assemblies allow the spacing of either one of the two forms, of both forms or of none of the forms.
 6. The device as claimed in claim 5, further comprising a stepping motor shaft, a stepper motor thereon, a first clockwise transmitting unidirectional clutch on one side of the stepper motor, said first clutch transmitting clockwise torque to the drive roll, and a second, counterclockwise transmitting unidirectional clutch on the other side of said stepper motor, said second clutch transmitting counterclockwise torque to the open/close cam shaft. 